Cross roll machines



June 6, 1961 w. M. Mcco 2,987,096

IN CROSS ROLL MACHINES Filed March 11, 1959 6 Sheets-Sheet 1 1N VENTOR. William M. McConnell BY W QL MAJ; 15W

HIS ATTORNEYS June 6, 1961 Filed March 11, 1.959

W. M. M CONN ELL CROSS ROLL MACHINES 6 Sheets-Sheet 2 INVENTOR. Will/am M. McConnell H/S ATTORNEYS June 6, 1961 w. M. MOCONNELL CROSS ROLL. MACHINES o .9 3 M mm M II 0 m m h M Q. m. m M w m h 5 U 6 H w W Y B m w H l l h m a M d e l 1 F HIS ATTORNEYS June 6, 1961 w. M. M CONNELL 2,987,096

CROSS ROLL MACHINES Filed March 11, 1959 6 Sheets-Sheet 4 ill Illllll INVENTOR. William M. McConnell BY 16W HIS ATTORNEYS June 6, 1961 w. M. MCCONNELL CROSS ROLL MACHINES 6 Sheets-Sheet 5 Filed March 11, 1959 L; AR mm kw INVENTOR. Wi/liam M. McConnell HIS ATTORNE Y5 June 6, 1961 w, MCCONNELL 2,987,096

CROSS ROLL MACHINES Filed March 11, 1959 6 Sheets-Sheet 6 I T F v IO I0 3 m IO Q o d- 9 0: 1-0 s a w m 0( g P 6:, o b3 0 m 1 m Q g 9 0: INVENTOR.

William M. McConnell BY i? 4 H/S A TTORNE Y5 fates This invention relates to cross roll machines which straighten and round lengths of tubular and round stock such as pipe, bars, rod, shafts and tubes.

Generally, cross roll machines comprise several stands of cross rolls arranged in tandem with a length of round stock traveling successively through each stand. As the length of stock advances through the stands, it is rotated about its longitudinal axis.

A cross roll stand usually has two rolls but some have four rolls and the rolls are adjustable toward and away from each other to define or form a pass therebetween through which the length of stock travels. The rolls are disposed so that their faces which engage the length of stock are crosswise of the center line of the pass.

In recent years, a 3-stand cross roll machine has proved successful with the second or middle stand having its rolls and the center line of its pass offset relative to the center line of the pass and the rolls of the first and third stands. The purpose of offsetting the pass of the middle stand is to introduce bending to the pipe and bring about a straightening of the length of the pipe and where the stock is ovaled, a rounding thereof.

In straightening and rounding lengths of pipe it is, of course, necessary to exceed the yield strength of the pipe but it is highly important that the yield strength be exceeded only an amount required to straighten and round the pipe. If, in straightening and rounding pipe unnecessarily high stresses or forces are imposed upon the Walls thereof, the ability of the pipe. to Withstand high external forces which buckle or collapse the pipe walls is materially reduced. These high external forces are frequently encountered in oil and gas operations where there is drilling many thousands of feet down in the ground at which place the pipe is subjected to high pressures from gas and oil at such levels beneath the surface of the earth. Accordingly, control over pipe straightening operations is desirable to avoid needless weakening of the pipe by use of excessively high forces when starightening and rounding.

Straightening of lengths of pipe on cross roll machines involves consideration of four factors. The first factor is the amount of bending imparted to the length of pipe. The second factor is the direction of bending. The third factor is the amount of pressure exerted by the cross rolls of each stand upon the Walls of the pipe; and the fourth factor is the amount of wear of each cross roll used on the straightening machine. Heretofore, an operator of a cross roll machine often'applied excessive stresses and forces when the effected straightening and rounding of the pipe. The excessive stresses resulted from experimentation in setting up a practice to straighten and round a particular lot of pipe, from not knowing the minimum amount of force required to straighten and round the pipe and from not knowing and having little or no control over the amount of. roll pressure actually used. Whenever he received a different lot of pipe for straightening or rounding, he again had to experiment in setting his machine and oftentimes in experimentation, subjected some of the lengths of pipe to excessive stresses. Even after experimentation produced a practice which straightened and rounded pipe, the practice in many instances subjected the pipe to high forces needlessly with resulting weakening of the pipe or tube walls.

2,987,096 Patented June 6, 1961 The operators experimentation to establish a practice to straighten and round a lot of pipe includes making adjustments for the amount of pressure exerted by the rolls, for the amount of bending imparted to a length of pipe and for roll wear. Some operators make no adjustment in their practice to compensate for roll wear. As between different operators on the same machine, practices have varied to the extent that one may use a large amount of bending with light roll pressure while another may use a small amount of bending with heavy roll pressure for the same size and kind of pipe. From the foregoing, it follows that operators of cross roll machines generally have no established practice for straightening and rounding a given lot of pipe.

One reason why there has been no established practice is because straightening machines have lacked provision for controlling amounts of pressure exerted by the roll, in some cases for controlling the amounts and direction of bending, and for compensating for roll Wear.

A comparison of practices for straightening and rounding butt welded pipe and seamless pipe shows that for butt welded pipe, there is a difierent amount of roll bending and a different amount of roll pressure needed for straightening and rounding as compared to that used for straightening and rounding seamless pipe of the same size. Specifically, one practice employed for straightening and rounding 1%." butt welded pipe welded pipe which has an outside diameter of 1.660 and a wall thickness of .140" is to pass the pipe through a 3-stand machine with the 3 stands having the rolls set to exert pressure and with the middle stand offset relative to the first and third stands. The amount of olfset is A; i.e., the center line of the pass between the two walls of the middle stand is offset A relative to the common center line of the first and third stands.

For butt welded pipe, the roll pressure for the first stand is 9,500 pounds per inch of roll contact. The roll pressure for the second stand is 16,600 pounds per inch of roll contact; and for the third stand, 9,500 pounds per inch of roll contact.

Straightening and rounding practice for 1%" seamless pipe is an offset of the second stand of W and a roll pressure in the first stand is 16,600 pounds per inch of roll contact. The roll pressure for the middle stand is 23,800 pounds per inch of roll contact and for the third stand, 9,500 pounds per inch of roll contact.

The practice for straightening and rounding 4" butt welded pipe is an offset for the middle stand of A" and a roll pressure in the first stand of 5,000 pounds per inch of roll contact. The roll pressure for the middle stand is 7,500 pounds per inch of roll contact and for the third stand, 3,500 pounds per inch of roll contact.

The straightening and rounding practices for 4 seam-- less pipe is an offset in the middle stand of A and a roll pressure in the first stand of 7,500 pounds per inch of roll contact. The roll pressure in the middle stand is 11,200 pounds per inch of roll contact and the third stand, 3,750 pounds per inch of roll contact. From the foregoing, it is apparent that straightening and rounding of pipe on straightening machines varies not only between different diameter pipe but also between butt welded pipe and seamless tubing. Consequently, ability to duplicate roll pressures and amounts of bending for successive straightening and rounding operations enables a pipe manufacturer to straighten and round substantially all pipe with minimum pressure and under regulated conditions, thereby easily producing pipe having high collapse and buckle strength.

Compensation for wear of cross rolls has been a problem of long standing in straightening machines. Of

course, the worn roll may be replaced by a new'one but if the straightening and rounding practice can be adjusted to compensate for roll wear, replacement of a cross roll after a small amount of wear is avoided with a consequent material reduction in cost of operation. Heretofore, some operators of straightening machines have attempted to allow for roll wear in their operation but have been unable to effectively compensate therefor; and, as a result, have subjected pipe surface to scuffing and marking and to production of flat spots thereon. In addition, ineffectual compensation of roll wear in straightening and rounding practices has brought about twisting of the pipe walls which is clearly undesirable and which weakens the walls.

In some cases where pipe has been badly bent and bent in more than, one plane, it is desirable to effect straightening by subjecting the pipe to bending in two planes as it travels through a straightening machine. The two planes are vertical and lateral relative to the path of travel of the pipe through the machine.

My straightening machine is adapted to carry out proven and established practices for straightening and rounding pipe and to easily duplicate the established practices. It carries out and duplicates the proven practices by control of the amount of pressure exerted by the cross rolls on a length of pipe traversing the machine, by regulating amounts and direction of bending and by providing bending in two planes relative to the path of travel of the pipe through the machine. In addition, my machine has provision for compensating for roll wear so that there is good contact of the cross rolls with the walls of the pipe as it advances through the machine. Specifically, my invention comprises three stands of cross rolls arranged in tandem so that a length of pipe travels successively through each stand. Each stand has at least two rolls which form a pass therebetween, a carrier for each roll located on the stand and a mounting which bears each roll and which is disposed on a carrier. The two carriers on a stand are spaced apart and at least one is movable toward and away from the other along a path of travel on its stand, thereby defining the pass between the two rolls. On a stand, the two rolls, the carriers and the mountings comprise an assembly.

At least one of the stands and preferably the second stand has a device for moving its assembly transversely of the machine relative to the center line of the pass of the machine formed by the rolls of the first and third stands. Thus the assembly of the second stand is oifset relative to the common center line of the pass of the first and third stands.

At least one of the mountings is movable on its carrier toward and away from the pass and the movement of the mounting is independent of the movement of its carrier. Connected to the mounting is a means for moving the mounting on its carrier.

At least one of the mountings has an eccentric member thereon disposed for rotation about an axis which is substantially parallel to the path of travel of its carrier member. A cross roll support is carried by the eccentric member and mounts thereon the cross roll. The cross roll support is rotatable upon its eccentric member.

Rotation of the eccentric about its axis of rotation imparts to the cross roll support and its cross roll movement substantially perpendicular to the path of travel of the carrier member and in a plane substantially perpendicular to the center line of the pass. Rotation of the cross roll support upon the eccentric member turns the cross roll about its axis disposed normal to the pass.

Positioned on each stand is a rod which extends in the direction of the path of travel of the carrier members. The rod carries two rod stops spaced apart and mounted thereon for travel toward and away from each other. One rod stop is so positioned on the rod that it indicates a position of one cross roll relative to the center line of the pass and the other rod stop is so positioned upon the rod that it indicates a position of the other cross roll relative to the center line of the pass. The rod has cooperating means for moving the two rod stops toward and away from each other to indicate a desired size of pass.

Connected to each carrier member and movable therewith is a carrier stop which is disposed to engage the rod stop upon movement of its carrier member toward the center line of the pass. Engagement of the carrier stop with the rod stop limits movement of the carrier member toward the center line of the pass. The position of the mounting on its carrier relative to the carrier stop is such that engagement of the carrier stop with the rod stop locates the cross roll at the position indicated by the rod stop and thereby forms a desired size of pass.

Connected to at least one of the carrier members is a fluid under pressure means which moves the carrier member along the path of travel. The fluid under pressure means provides a fluid under pressure backing for the cross roll or rolls to which it is associated. A control connected to the fluid under pressure means regulates the supply of fluid under pressure to the fluid under pressure means and its release therefrom, thereby controlling the amount of pressure exerted by the cross rolls upon the round stock traversing the machine.

In the accompanying drawings I have shown a preferred embodiment of my invention in which:

FIGURE 1 is a side elevation view of a 3-stand straightener machine incorporating my invention;

FIGURE 2 is a plan view of the straightening machine of FIGURE 1;

FIGURE 3 is a section view along the line IH-III of FIGURE 1;

FIGURE 4 is a plan view of a stand of the machine with the cross rolls and some parts of their mountings removed to show the rod, rod stop and carrier stops;

FIGURE 5 is a side elevation view of the mounting for a cross roll of a stand with the cross roll in one position;

FIGURE 6 is a section view along line VI-VI of FIGURE 5;

FIGURE 7 is a side elevation view similar to FIGURE 5 but showing the cross roll in a second position;

FIGURE 8 is a schematic diagram showing the fluid under pressure system connected to the stand of FIGURE 3; and

FIGURE 9 is a schematic diagram showing the electrical circuits which operate the motors driving the cross rolls of the machine of FIGURE 1.

The straightening machine of FIGURES I and 2 comprises three stands, 1, 2 and 3, arranged in tandem so that a length of pipe or tubing to be straightened and rounded passes consequently through stand 1, then through stand 2, and exits through stand 3. Of course the pipe may travel through the three stands in the reverse direction.

As shown in FIGURES 1-3 each stand comprises a base 4 upon which are disposed two cross rolls 5 and 6 spaced apart to form a pass 7 therebetween. In FIGURE 2, line 8 represents the center line of the pass through each of the three stands. Each roll is journaled in bearings 9 and driven by an electric motor 10 (FIGURE 9) connected thereto through shaft 11.

Referring to FIGURE 3, stand 2 has an oifset adjustment 12 for positioning a carriage 13 of stand 2 transversely of the center line 8 of the pass. The offset adjustment '12 acts upon the carriage 13 of the stand 2 which carriage is mounted on a slide 14 of the pass and moves along the slide in the direction of arrow 15 in response to operation of the adjustment.

The olfset adjustment comprises a shaft 16 extending through a threaded bore 17 in a block 18 aflixed to the base. The shaft 16 extends to the carriage 13 where a head 19 on one end of the shaft is joined to the carriage in a T-shaped slot 20. The shaft'16 has threads which engage those of the block so that the carriage can be moved along the slide 14 by rotation of the shaft about its longitudinal axis.

The carriage 13 has a pointer 21 connected thereto and disposed so that it is opposite a scale 22 on the block 18 whereby the amount of movement of the carriage along the slide is shown by the position of the pointer opposite a mark on the scale.

Disposed on the carriage 13 are two cross roll carriers 23 and 24, each mounting a cross roll. Each carrier is movable on ways 25 along a path of travel on the carriage toward and away from a vertical plane through the center line 8 of the pass. As shown in FIGURE 3, the two carriers have a rack and pinion arrangement 26 actuated by a hydraulic cylinder 27 whose piston rod 28 extends through the cylinder into engagement with part 29 of the rack. Operation of the rack and pinion by the hydraulic cylinder causes the two carriers to simultaneously move to and from a desired position relative to the center line 8 of the pass.

The hydraulic cylinder 27 in addition to effecting travel of the two carriers along the carriage 13 provides a fluid under pressure backing for the cross rolls, thereby permitting the operator of the machine to use only that amount of pressure exerted by the rolls to effect straightening and rounding of a length of pipe. Each of the stands 1 and 3 also has the hydraulic cylinder 27 for advancing and withdrawing the cross rolls of those stands relative to the center line 8.

FIGURE 8 shows a conventional fluid under pressure system 30 which is connected to each cylinder 27. This fluid under pressure system comprises a tank 31 from which a pump 32 driven by motor 33 delivers fluid under pressure to a 4-way solenoid operated valve 34. From the 4-way valve, fluid under pressure flows through conduit 35 to the cylinder when it is desired to actuate the piston rod 28 to move the carriers toward one another along the path of travel. To move the carriers apart from a given position to accommodate a larger size pipe, the 4-way valve 34 is operated so that fluid under pressure enters the cylinder 27 through conduit 36 and escapes therefrom through conduit 35 to the 4-way valve and back to the tank 31 through pipe 37. Connected to the pump 32 is a pressure regulating valve 38 which enables one to control the amount of pressure used in the fluid under pressure system and in the cylinder. By use of the pressure regulating valve, I can control the amount of pressure exerted by the cross rolls 5 and 6 upon the round stock traveling through the straightener machine.

On each carrier is a mounting 39 which supports a cross roll and which is movable along its carrier on a slide 40 toward and away from the center line 8 of the pass. Movement of the mounting 39 along the slide 40 is independent and separate from travel of the carrier resulting from actuation of the cylinder 27. A shaft 41 threaded at one end 41a and journaled on a post 42. of the carriers 23 and 24 (FIGURE 3) advances and withdraws the mounting 39 relative to the center line 8 which is represented as point 8 in FIGURE 3 for it is normal to the plane of FIGURE 3. The threaded end of the shaft extends through a threaded bore 43 of an upright 44 of the mounting. The upright has a scale 45 positioned opposite a pointer 45 which is aflixed to the post 42. The scale 45 has markings which indicate diameter of the cross roll and its use will be discussed more in detail hereinafter. Rotation of the shaft 41 about its longitudinal axis positions the mounting on its carrier and in this way, one compensates for wear of the cross roll as will be discussed herein.

Referring to FIGURES 3, 5, 6 and 7, the mounting 39 comprises a housing 47 having an opening 48 extending therethrough. As shown in FIGURE 3, the housing is disposed upright on the mounting 39 and on the carriers 23 and 24. Located in the opening 48 upon a bushing 49 is an eccentric 50 having a bore 51 extending therethrough. The eccentric is rotatable upon the bushing 49 in the housing about its axis of rotation which is parallel to the path of travel of the carrier on the slide 25. In the bore 51 of the eccentric is a second bushing 52 upon which is a disk plate 53 to which is aflixed the bearings 9 which carry the cross roll 5 or 6. The disk plate 53 is in engagement with face 54 of the eccentric 50 and face 55 of the housing 47 and extends along the face 54 of the eccentric and along the face 55 of the housing. The disk plate is rotatable upon the bushing 52 independently of rotation of the eccentric and the axis of rotation of the disk plate is parallel to the axis of rotation of the eccentric.

As shown in FIGURES 5 and 6, connected to the upper part of the disk plate is a projection 56. Straddling the projection 56 are two stop bolts 57 and 58 mounted on lugs 59 and 60 of the housing 47.

Both the eccentric 5t) and the projection 56 of the disk plate have receptacles 61 which receive the end of a wrench rod for turning the eccentric and the disk plate about their respective axes of rotation.

Rotation of the eccentric about its axis of rotation raises or lowers the cross roll viewing FIGURES 3 and 6. The purpose for raising or lowering the cross roll by operation of the eccentric is to provide bending of a length of pipe traveling through the stand in a second plane, namely, in a plane disposed vertical to the pass formed by the two cross rolls.

Rotation of the disk plate about its axis of rotation effects a turning of the cross roll 5 or 6 about an axis disposed normal to the surface of the round stock traveling through the pass 7. Ability to turn the cross roll about this axis permits one to position a cross roll at different angles crosswise to the pass 7 and to the longitudinal axis of the round stock.

There is a slot 62 formed by the housing 47, the eccentric 50, and two strip members 63 and 64 which are connected to two lugs 65 and 66 on the housing. The slot 62 is bounded on the top and bottom viewing FIG URES 5, 6 and 7 by two lugs 65 and 66 and bounded on the sides by the housing. The slot extends from the lugs 65 and 66 down into the eccentric 50 as shown in FIGURE 6 and is located perpendicular to the axis of rotation of the eccentric and of the disk plate.

Disposed in the slot and movable therein are a frame 67 and an inside plate 68 with a central bore 69 extending through the inside plate. The inside plate is located within the frame 67 in the slot 62 and the housing 47 and the frame 67 limit movement of the inside plate in the slot to a path perpendicular to the path of movement of the frame in the slot. The lugs 65 and 66 and the sides of the housing limit the path of movement of the frame 67 in the slot to movement in a plane located at substantially right angles to the center line 8 of the pass. Thus within the slot 62 movement of the frame is restricted to vertical travel viewing FIGURE 5 as shown by arrow 76 while the movement of the inside plate in the slot is restricted to horizontal travel viewing FIGURE 5 as indicated by arrow 71.

Rotation of the eccentric 50 about its axis of rotation imparts movement to both the frame along its restricted path and to the inside plate along its restricted path. In other words, viewing FIGURE 5, as the eccentric 50 is rotated about its axis of rotation in a clockwise direction, the frame 67 moves downwardly viewing FIG- URE 5 while the inside plate moves to the right viewing FIGURE 5. Because of frictional contact between the face of the eccentric and the face of the disk plate, rotation of the eccentric imparts a rotation to the disk plate with the amount of rotation of the disk plate generally being less than that of the rotation of the eccen- On the strip member 64 is a scale 72 positioned op posite the bottom part of the frame 67. The markings on the scale indicate the amount of raising and lowering of the cross roll viewing FIGURES 3 and 5 which result from turning of the eccentric about its axis of rotation. By observing the position of the bottom part of the frame relative to the scale 72, one can accurately know how much to turn the disk plate to raise or lower the cross roll.

As shown in FIGURES 1, 3 and 5, the cross rolls are positioned crosswise relative to the pass and the ability of the disk plate 53 to be turned enables one to set the rolls at diiferent crosswise positions. When the cross rolls have been set at a desired crosswise position by turning the disk plate, the stop bolts 57 and 58, which have been first withdrawn from engagement with the projection 56, are turned about their longitudinal axes to bring them into engagement with the projection and thereby lock the cross rolls in the desired crosswise position. Naturally when it is desired to change the position of the cross roll, the stop bolts must be withdrawn from engagement with the projection.

As shown in dash lines in FIGURE 5, the cross roll 5 is disposed at a selected crosswise position and the angle of positioning of the cross roll is indicated by a reference mark 73 on the inside plate 68. This reference mark is parallel to the longitudinal axis 74 of the cross roll viewing FIGURE 5. When the eccentric 50 has been rotated to raise or lower the cross roll, the disk plate usually has been rotated in the direction of rotation of the eccentric so that the cross roll 5 no longer is at the angle shown in FIGURE 5. Because the inside plate can only travel in a horizontal path, viewing FIGURE 5, upon rotation of the eccentric the reference mark 73 is at the same angle as occupied originally by the cross roll prior to rotation of the eccentric. Accordingly, the reference mark and an indicator 75 are used to enable one to return the cross roll to its original crosswise position. The indicator 75 is affixed to the disk plate and rotatable therewith. The indicator 75 has on its pointing end a scale 75a which is located opposite the reference mark '73. Therefore, since the pointer rotates the same amount as the disk plate when the eccentric has been turned and turns in the same direction, the scale on the pointer indicates the amount which the cross roll has been turned away from its position shown in FIGURE 5. Thus, one can quickly return the cross roll to its original crosswise position by rotating the disk plate in the opposite direction until the reference mark is opposite the mark on the scale which was opposite the reference mark prior to rotating the eccentric.

FIGURE 7 shows in dash lines the position of the pointer relative to the reference mark after rotation of the eccentric. FIGURE 7 also shows the position of the frame 67 relative to the scale 72 and the amount of lowering of the cross roll resulting from rotating the eccentric.

A clamp 76 in combination with a bolt '77, washer 78, nut '79 and head 8i hold the eccentric 50 and disk plate 53 together and in position on the housing 47. This clamp also assists in maintaining the frame and inside plate within the slot 62. The bolt extends through an opening 81 in the clamp 76 through a bore of the disk plate and terminates in the head 80 disposed in a recess 82 in the disk plate.

FIGURE 9 shows conventional electric circuits $3 for operating the electric motors 16 which drive the cross rolls. As shown, there is an electric motor for each cross roll with motors 10, Illa, liib, The, 10d and 10a driving respectively rolls 5, 5a, 5b, 6, 6a and 6b. A direct current main generator $4 operates each of the motors which drive the cross rolls. The main generator is driven by an A.C.'motor 85 and comprises a conventional motor generator set. Each of the motors is a reversible, variable speed type whereby control of the speed of straightening and rounding pipe can be carefully regulated. Because the 3-stand straightener can use different diameter rolls and effect compensation for roll Wear, each roll is driven by a motor whose operation is separate and independent from the operation of the other motors which drive the other rolls. Rheostats 86 provide control over the motors 10. Hydraulic motors (not shown) may be substituted for the electric motors 10.

Referring to FIGURES 3 and 4, there is a rod 87 which extends substantially the length of the base and has its ends mounted in bearings 88 positioned upon the carriage 13 in the case of stand 2 and upon the base 4 in the case of stands 1 and 3. A sprocket 89 affixed to one end of the rod 87 in combination with a chain 90, motor 91 and motor driven sprocket 92 turn the rod about its longitudinal axis. A center part of the rod is journalcd in a block 93 located upon the carriage of stand 2 and upon the base of stands 1 and 3. As shown, the rod 87 is located below the pass 7.

The rod 87 carries two rod stops 94 and 95 mounted thereon for travel towards and away from the block 93 which is directly beneath the pass formed by the two cross rolls. As shown, the rod stops are spaced apart and one stop engages left-hand threads on the rod and the other rod stop engages right-hand threads thereon so that upon rotation of the rod about its longitudinal axis, the two stops move simultaneously toward each other or simultaneously away from each other, depending upon rotation of direction of the sprocket 89. Connected to each end of the rod stops is a guide shaft 96 which extends through the housing 47 of the mounting and along which the housing travels when the carriage and the mounting are moved toward and away from the pass.

The rod stops are located along the rod so that rod stop 94 indicates a position of the cross roll 5 relative to the center line 8 of the pass and so that rod stop 95 indicates the position of the cross roll 6 relative to the center line 8. Thus when the rod stops are moved, their position indicates a larger or smaller pass, depending upon the direction of movement relative to the center line 8 and the rod stops enable an operator of the straightener to quickly and accurately position the cross rolls to form the desired size of pass as will be described herein. A dial 97 and pointer 98 indicate the position of the rod stops along the rod 87.

Connected to each carrier through guide bars 99 and 100 is a carrier stop 101. One end of each of the guide bars is afiixed to the carrier and the other end is afiixed to the carrier stop. The guide bars extend through the mounting '39 which is slidable therealong.

The carrier stop is located on the stand so that upon travel of the carrier toward the center line 8 of the pass, the carrier stop 191 engages the rod stop 94 or 95, and movement of the cross roll toward the center line 8 is terminated. Engagement of the carrier stop with the rod stop locates the cross roll at the position indicated by the rod stop and determines the size of the pass. Thus by operation of the hydraulic cylinder 27, the two carriers are moved simultaneously along their path of travel on the carriage or base, as the case may be, until the carrier stop engages the rodstop, whereupon the cross rolls are positioned to form the desired size of pass.

Each of stands 1, 2 and 3 has ability to position the cross rolls in order to compensate for roll wear. Referring to FIGURES 3 and 4, rotation of shaft 41 advances or withdraws the mounting relative to the center line 8, depending upon direction of rotation of the shaft about its longitudinal axis. When a new roll is placed on the bearin gs 9, the shaft is turned to locate the mounting on its carrier so that when the carrier stop engages the rod stop, the roll is in position to form a desired size of pass. In other Words, the shaft 41 is operated to set the mounting 39 on its carrier so that there is a required spacing between the face 102 of the roll which engages a length of stock traveling through the pass 7 and the face 103 of the carrier stop which engages the face 104 of the rod stop. When the mounting is so located on its carrier, the pointer 46 is opposite a marking on the scale 45 and there is the required spacing between the face of the roll which contacts a pipe in the pass and the face of the carrier stop which engages the rod stop. Thus, the cross roll is positioned on the carrier so that when the carrier stop has engaged the rod stop, the cross roll is at the desired position to form a given size of pass.

As the roll wears, its diameter naturally becomes smaller and the required spacing also becomes smaller, whereupon the shaft 41 is turned to advance the mounting on its carrier towards the center line 3 an amount sufficient to restore the required spacing and bring the mounting to a position on its carrier whereby when the carrier stop has engaged the rod stop, the roll is once again at a position which forms a given size of pass. Consequently, as the roll continues to wear and its diameter becomes smaller, the shaft 41 is operated to move the mounting towards the center line 8 on its carrier and to restore the required spacing.

By use of the scale 45 and pointer 46, the amount of advancement of the mounting on its carrier to restore the required spacing can be easily determined. In this way, I can compensate for roll wear in setting up practice for straightening and rounding pipe and thus realize materially increased life for the rolls without experiencing the disadvantages of worn rolls in operation of the machine which may produce scuffed or marked surfaces, flat spots and twisted pipe walls.

As shown in FIGURES 3 and 4, there is a small gap 105 between the carrier stop 1G1 and the housing 47. This gap is at a maximum when a new roll is in the bearings 9 and as the roll wears and the shaft 41 is operated to maintain the required spacing, the gap be comes smaller until the housing engages the rear face 106 of the carrier stop, whereupon the roll has been so badly worn that a new one is required.

Operation of the three stands comprises positioning the carriage of stand 2 so that there is a desired amount of offset. Eifecting this offset results from rotating the shaft 16 the necessary amount to move the carriage, carrier and mountings of stand 2 to the right or left, viewing FIGURE 3. The amount of offset is determined by the diameter of the round stock and whether it is butt welded pipe, seamless tubing, etc. Then the rod stops are positioned to govern the specified size of pass. Next, the hydraulic cylinders of each stand are actuated to bring the carriers to the position determined by the position of the rod stops, whereupon the cross rolls form the desired size of roll pass. Of course, before the hydraulic cylinders are actuated to position the cross rolls, each cross roll has been positioned on its carrier by operation of the shaft 41 to take into account roll wear and to insure that the required spacing between the face 103 of the carrier stop and the face 102 of the cross roll which engages the pipe has been accurately established. Before or after positioning of the rolls by the hydraulic cylinder, the eccentric is operated to raise or lower the cross rolls and the disk plate is turned to position each cross roll at a desired crosswise position relative to the center line of the pass. After the hydraulic cylinder has positioned the cross rolls, after the rolls have been raised or lowered by the eccentric and turned by the disk plate to locate them crosswise of the pass, the motors are started and the three stands are ready to straighten and round pipe.

My straightener is a versatile machine for it can effect straightening and rounding of pipe by bending the pipe in two planes, one vertical and the other lateral, to the center line of the pass. Bending of the pipe in a vertical plane relative to the pass results from operation of the eccentric and bending of the pipe in the lateral plane relative to the pass results from turning the shaft 16 to offset stand 2. Of course, the offset arrangement can be installed on any of the three stands. I can effect bending of the pipe between two stands in both the vertical and lateral planes where at least one of the two stands has the offset feature and where each of the stands has the eccentric. Ability to bend the pipe in two planes enables one to straighten pipe which has been badly bent and which has been bent in two planes.

An important advantage of my straightener machine is that one can use it for establishing and carrying out the best practices for straightening and rounding pipe. Practices which can be performed by my machine include those which require controlled amounts of bending in one and/or in two planes and controlled amounts of pressure exerted by the rolls upon the pipe. The offset arrangement in combination with the eccentric enables one to produce bending in one and/ or two planes and to control the amount of bending. The hydraulic cylinder enables one to control the amount of pressure exerted by the rolls upon the pipe. Thus my invention provides a straightener which can reproduce easily established practices which subject pipe to a minimum of stress and thus results in production of pipe able to withstand high collapsing and buckling forces.

In the event there is a wreck or cobble on my machine, the rack and pinion arrangement quickly and easily withdraws the cross rolls from the pipe and permits fast clearing of the pipe from the machine.

My cross roll machine has a significant advantage, namely, for different size pipe, ability to adjust the bottom of a pass line to a constant elevation relative to entry and delivery tables. These entry and delivery tables bring pipe to be straightened to my machine and remove the straightened pipe therefrom. Consequently, vertical adjustment of the entry and delivery tables for different size pipe and/ or for wear of rolls of the entry and delivery tables is eliminated. This advantage results from the use of the eccentric 50 to raise or lower a cross roll.

While I have described a presently preferred embodiment of my invention, it is to be understood that it may be otherwise embodied within the scope of the following claims.

I claim:

1. On a cross roll straightener stand having a base and at least two cross rolls, the combination comprising two mounting means each mounting one cross roll, said mounting means being spaced apart and at least one mounting means being movable toward and away from the other along a path of travel on the straightener stand so that the cross rolls form a pass therebetween for travel of stock therethrough, at least one of said mounting means having a member adapted for imparting to the cross roll, movement which is substantially perpendicular to said path of travel of said movable mounting means and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line of said pass and which is in a plane substantially perpendicular to the center line of said pass and means for moving said movable mounting means along the path of travel.

2. The combination of claim 1 characterized by at least one of said mounting means comprising a fixed member, an eccentric member thereon and disposed for rotation about an axis which is substantially parallel to said path of travel, a cross roll support carried by said eccentric member and bearing the cross roll, rotation of said eccentric about its axis of rotation imparting to the cross roll support and its cross roll movement which. is substantially perpendicular to said path of travel and which is in a plane substantially perpendicular to the center line of the pass.

3. The combination of claim 1 characterized by at least one of said mounting means having a fixed member, an eccentric member thereon and disposed for rotation about an axis located parallel to said path of travel, a

cross roll support carried by said eccentric member and bearing a cross roll, said cross roll support being rotat able on said eccentric member, rotation of said eccentric member about its axis of rotation imparting to the cross 'roll support and its cross roll movement which is substantially perpendicular to said path of travel and which is in a plane substantially perpendicular to the center line of the pass, rotation of the cross roll support on the eccentric member turning the cross roll about an axis disposed normal to said pass.

4. On a cross roll straightener stand having a base and at least two cross rolls, the combination comprising two mounting means each mounting a cross roll, and being spaced apart, at least one of said mounting means being movable toward and away from the other along a path of travel on the straightener stand so that the cross rolls form a pass therebetween for travel of stock therethrough, at least one of said mounting means having a fixed member, an eccentric member thereon disposed for rotation about an axis located parallel to said path of travel, each mounting means having a cross roll support bearing the cross roll, rotation of said eccentric member about its axis of rotation imparting to the cross roll support and its cross roll movement which is substantially perpendicular to said path of travel and which is in a plane substantially perpendicular to the center line of the pass, a slot formed by the fixed member and the eccentric member, said slot being substantially perpendicular to the axis of rotation of the eccentric member, a frame member and an inside member with a central bore therethrough disposed in said slot and movable therein, said inside member being located inside the frame member, said fixed member and said eccentric member limiting movement of the frame to a path in said slot in a plane which is disposed substantially at right angles to said path of travel, said frame member and said fixed member limiting movement of the inside member to a path in the slot perpendicular to that of the path of movement of the frame, a reference mark on said inside member, said reference mark indicating a given position of the cross roll on its support, said given position being determined by turning the cross roll about an axis which is disposed substantially normal to the pass, and pointer means affixed to the cross roll support and rotatable therewith, said pointer means being positioned adjacent the reference mark and having a scale thereon to indicate amount of turning of said cross roll about said axis normal to the pass relative to the given position and means for moving said movable mounting means along said path of travel.

5. The combination of claim 4 characterized by said fixed member having scale means adjacent said slot and positioned opposite the path of movement of said frame in said slot for indicating position of the cross roll in its path of travel resulting from rotation of the eccentric member about its axis of rotation as shown by position of a part of said frame relative to the scale means.

6. On a cross roll straightener stand having a base and at least two cross rolls, the combination comprising two mounting means each mounting one cross roll, said mounting means being spaced apart and at least one mounting means being movable toward and away from the other along a path of travel on the straightener stand so that the cross rolls form a pass therebetween for travel of stock thereihrough, at least one of said mounting means having a member adapted for imparting to the cross roli, movement which is substantially perpendicular to said path of travel of said movable mounting means and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line of said pass and which'is in a plane substantially perpendicular to the center line of said pass, fluid under pressure motor having a member oined thereto for transmitting power generated thereby, said member being directly connected to said movable mounting means for moving it along said path of travel, said fluid under pressure motor providing a controlled fluid under pressure backing for the cross roll of said movable mounting means and means connected to said fluid under pressure motor for controlling the supply of fluid under pressure to said fluid under pressure motor and its relief therefrom and for regulating the amount of pressure exerted by the cross rolls upon round stock traversing the pass.

7. On a cross roll straightener stand having a base and at least two cross rolls, the combination comprising two mounting means each mounting a cross roll, and being spaced apart, at least one of said mounting means being movable toward and away from each other along a path of travel on the straightener stand so that the cross rolls form a pass therebetween for travel of stock therethrough, at least one of said mounting means having a fixed member, an eccentric member thereon disposed for rotation about an axis located parallel to said path of travel, each mounting means having a cross roll support bearing the cross roll, rotation of said eccentric member about its axis of rotation imparting to the cross roll support and its cross roll movement which is substantially perpendicular to said path of travel of said movable mounting means and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially paral lel to and laterally of the center line of said pass and which is in a plane substantially prependicular to the center line of the pass, a slot formed by the fixed member and the eccentric member, said slot being substantially perpendicular to the axis of rotation of the eccentric member, a frame member and an inside member disposed in said slot and movable therein, said inside member being located inside the frame member, said fixed member and said eccentric member limiting movement of the frame to a path in said slot in a plane which is disposed substantially at right angles to the center line of the pass, said frame member and said fixed member limiting movement of the inside member to a path in the slot perpendicular to that of the path of movement of the frame, a reference mark on said inside member, said reference mark indicat ing a given position of the cross roll on its support, said given position being determined by turning the cross roll about an axis which is disposed substantially normal to the pass, pointer means affixed to the cross roll support and rotatable therewith, said pointer means being positioned adjacent the reference mark and having a scale thereon to indicate amount of turning of said cross roll about said axis normal to the pass relative to the given position, fluid under pressure motor having a member joined thereto for transmitting power generated thereby, said member being directly connected to said movable mounting means for moving it along said path of travel and for providing a controlled fluid under pressure backing for the cross roll of said movable mounting means and means connected to said fluid under pressure motor for controlling the supply of fluid under pressure to said fluid under pressure motor and its relief therefrom and for regulating the amount of pressure exerted by the cross rolls upon round stock traversing said pass.

8. On a cross roll straightener stand having a base and at least two cross rolls, the combination comprising two carrier members disposed on said base and spaced apart thereon, a mounting means bearing a cross roll on each carrier member, said carrier members being movable toward and away from the other along a path of travel on the straightener stand so that the cross rolls form a pass therebetween for travel of stock therethrough, means for moving said movable carrier members along the path of travel, rod means disposed on said base and extending in the direction of said path of travel, said rod means carrying two rod stop members spaced apart and mounted thereon for travel toward and away from each other upon rotation of said rod about its longitudinal axis, one rod stop member being so disposed on said rod means that it indicates a position of one cross roll relative to the center line of said pass, the other rod stop member being so located on said rod means that it indicates a position of the other cross roll relative to the center line of the pass, cooperating means connected to said rod means for rotating said rod means about its longitudinal axis to move the rod stop member toward and away from each other to indi cate a desired pass, a carrier stop connected to each carrier member and movable therewith, said carrier stop being disposed to engage said rod stop member upon movement of its carrier member toward the center line of said pass, engagement of said carrier stop with said rod stop member limiting movement of said carrier member toward the center line of said pass, the position of said mounting means on said carrier relative to said carrier stop being such that engagement of the carrier stop with the rod stop locates the cross roll at the position indicated by the rod stop member and thereby forms a desired size of pass.

9. On a cross roll straightener stand having a base and at least two cross rolls, the combination comprising two carrier members disposed on said base and spaced apart thereon, a mounting means bearing a cross roll on each carrier member, said carrier members being movable toward and away from the other along a path of travel on the straightener stand so that the cross rolls form a pass therebetween for travel of stock therethrough, rod means disposed on said base and extending in the direction of said path of travel, said rod means carrying two rod stop members spaced apart and mounted thereon for travel toward and away from each other upon rotation of said rod about its longitudinal axis, one rod stop member being so disposed on said rod means that it indicates a position of one cross roll relative to the center line of said pass, the other rod stop member being so located on said rod means that it indicates the position of the other cross roll relative to the center line of said pass, cooperating means connected to said rod means for rotating said rod means about its longitudinal axis to move the rod stopmembers toward and away from each other to indicate a desired pass, a carrier stop connected to each carrier member and movable therewith, said carrier stop being disposed to engage said rod stop member upon movement of its carrier member toward the center line of said pass, engagement of said carrier stop with said rod stop member limiting movement of said carrier member toward the center line of said pass, the position of said mounting means on said carrier relative to said carrier stop bieng such that engagement of the carrier stop with the rod stop locates the cross roll at the position indicated by the rod stop member and thereby forms a desired size of pass, fluid under pressure motor having a member joined thereto for transmitting power generated thereby, said member being connected to said movable carrier members for moving them along said path of travel and for providing a controlled fluid under pressure backing for the cross roll of said movable carrier members and means connected to said fluid under pressure motor for controlling the supply of fluid under pressure to said fluid under pressure motor and its relief therefrom and for regulating the amount of pressure exerted by the cross rolls upon round stock traversing said pass.

10. The combination of claim 6 characterized by at least one of said mounting means comprising a fixed member, an eccentric member thereon disposed for rotation about an axis substantially parallel to said path of travel, a cross roll support carried by said eccentric member and bearing the cross roll, rotation of said eccentric about its axis of rotation imparting to the cross roll support and its cross roll movement which is substantially perpendicular to said path of travel of said movable mounting means and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line dicular to the center line of the pass.

11. The combination of claim 6 characterized by at least one of said mounting means having a fixed member, an eccentric member thereon disposed for rotation about an axis substantially parallel to said path of travel, a cross roll support carried by said eccentric member and bearing a cross roll, said cross roll support being rotatable on said eccentric member, rotation of said eccentric member about its axis of rotation imparting to the cross roll support and its cross roll movement which is substantially perpendicular to said path of travel of said movable mounting means and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line of said pass and which is in a plane substantially perpendicular to the center line of the pass, rotation of the cross roll support on the eccentric member turning the cross roll about an axis disposed normal to said pass.

12. The combination of claim 8 characterized by at least one of said mounting means having a member adapted for imparting to its cross roll movement which is substantially perpendicular to said path of travel of said movable carrier members and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line of said pass and which is in a plane substantially perpendicular to the center line of the pass.

13. The combination of claim 8 characterized by at least one of said mounting means comprising a fixed member, an eccentric member thereon disposed for rotation about an axis substantially parallel to said path of travel, a cross roll support carried by said eccentric member and bearing the cross roll, rotation of said eccentric about its axis of rotation imparting to the cross roll support and its cross roll movement which is substantially perpendicular of said path of travel of said movable carrier members and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line of said pass, and which is in a plane substantially perpendicular to the center line of the pass.

14. The combination of claim 8 characterized by at least one of said mounting means having a fixed member, an eccentric member thereon disposed for rotation about an axis substantially parallel to said path of travel, a cross roll support carried by said eccentric member and bearing a cross roll, said cross roll support being rotatable on said eccentric member, rotation of said eccentric member about its axis of rotation imparting to the cross roll support and its cross roll movement which is substantially perpendicular to said path of travel of said movable carrier members and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line of said pass and which is in a plane substantially perpendicular to the center line of the pass, rotation of the cross roll support on the eccentric member turning the cross roll about an axis disposed normal to said pass.

15. The combination of claim 9 characterized by at least one of said mounting means having a member adapted for imparting to its cross roll movement which is substantially perpendicular to said path of travel of said movable carrier members and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line of said pass and which is in a plane substantially perpendicular to the center line of said pass.

16. The combination of claim 9 characterized by at least one of said mounting means comprising a fixed member, an eccentric member thereon disposed for rotation about an axis substantially parallel to said path of travel, a cross roll support carried by said eccentric member and bearing the cross roll, rotation of said eccentric about its axis of rotation imparting to the cross roll support and its cross roll movement which is substantially perpendicular of said path of travel of said a 15 movable carrier members and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line of said pass, and which is in a plane substantially perpendicular to the center line of the pass.

17. The combination of claim 9 characterized by at least one of said mounting means having a fixed member, an eccentric member thereon disposed for rotation about an axis substantially parallel to said path of travel, a cross roll support carried by said eccentric member and bearing a cross roll, said cross roll support being rotatable on said eccentric member, rotation of said eccentric member about its axis of rotation imparting to the cross roll support and its cross roll movement which is substantially perpendicular to said path of travel of said movable carrier members and which is substantially laterally of said pass and substantially perpendicular to a line disposed substantially parallel to and laterally of the center line of said pass, and which is in a plane substantially perpendicular to the center line of the pass, and rotation of the cross roll support on the eccentric member turning the cross roll about an axis disposed normal to said pass.

18. The combination of claim 8 characterized by at least one of said mounting means being movable on its carrier toward and away from said pass independently of movement of its carrier and means for moving said movable mounting on its carrier.

19. The combination of claim 9 characterized by at least one of said mounting means being movable on its carrier toward and away from said pass independently of movement of its carrier and means for moving said movable mounting on its carrier.

References Cited in the file of this patent UNITED STATES PATENTS 86,098 Parker Jan. 19, 1869 450,234 Johnson Apr. 14, 1891 1,713,138 Leek May 14, 1929 1,887,434 Sammis Nov. 8, 1932 2,017,972 Isbell Oct. 22, 1935 2,180,046 Gleissner Nov. 14, 1939 2,209,337 Kane July 30, 1940 2,271,783 Sutton Feb. 3, 1942 2,517,344 Picton Aug. 1, 1950 FOREIGN PATENTS 598,757 Great Britain Feb. 25, 1948 

